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Modelling and assembly of the full vehicle 381 30 m 25 m 25 m 30 m 15 m A C B A – 1.3 times vehicle width 0.25 m B – 1.2 times vehicle width 0.25 m C – 1.1 times vehicle width 0.25 m Fig. 6.49 Lane change test procedure. (This material has been reproduced from the Proceedings of the Institution of Mechanical Engineers, K2 Vol. 214 ‘The modelling and simulation of vehicle handling. Part 4: handling simulation’, M.V. Blundell, page 74, by permission of the Council of the Institution of Mechanical Engineers) 120.0 STEERING INPUT – 100 km/h LANE CHANGE Steering wheel angle (deg) 80.0 40.0 0.0 40.0 80.0 120.0 0.0 1.0 2.0 3.0 4.0 Time (s) Fig. 6.50 Steering input for the lane change manoeuvre 5.0 vehicle dynamics task, however, the automotive engineer will want to carry out simulations before the design has progressed to such an advanced state. In this case study the level of vehicle modelling detail required to simulate a ‘full vehicle’ handling manoeuvre will be explored. The types of manoeuvres performed on the proving ground are discussed in the next chapter but as a start we will consider a 100 km/h double lane change manoeuvre. The test procedure for the double lane change manoeuvre is shown schematically in Figure 6.49. For the simulations performed in the case study the measured steering wheel inputs from a test vehicle have been extracted and applied as a time dependent handwheel rotation (Figure 6.50) as described in section 6.12.3.
382 Multibody Systems Approach to Vehicle Dynamics Fig. 6.51 Superimposed graphical animation of a double lane change manoeuvre To appreciate the use of computer simulations to represent this manoeuvre an example of the superimposed animated wireframe graphical outputs for this simulation is given in Figure 6.51. In this study the influence of suspension modelling on the accuracy of the simulation outputs is initially discussed based on results obtained using the four vehicle models described in section 6.4 and summarized schematically again here in Figure 6.52. The models shown can be thought of as a set of models with evolving levels of elaboration leading to the final linkage model that involves the modelling of the suspension linkages and the bushes. For each of the vehicle models described here it is possible to estimate the model size in terms of the degrees of freedom in the model and the number of equations that MSC.ADAMS uses to formulate a solution. The calculation of the number of degrees of freedom (DOF) in a system is based on the Greubler equation given in Chapter 3. It is therefore possible for any of the vehicle models to calculate the degrees of freedom in the model. An example is provided here for the equivalent roll stiffness model where the degrees of freedom can be calculated as follows: Parts 9 6 54 Rev 8 5 40 Motion 2 1 2 Σ DOF 12 In physical terms it is more meaningful to describe these degrees of freedom in relative terms as follows. The vehicle body part has 6 degrees of freedom. The two axle parts each have 1 rotational degree of freedom relative to the
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382 Multibody Systems Approach to Vehicle Dynamics<br />
Fig. 6.51 Superimposed graphical animation of a double lane change<br />
manoeuvre<br />
To appreciate the use of computer simulations to represent this manoeuvre<br />
an example of the superimposed animated wireframe graphical outputs for<br />
this simulation is given in Figure 6.51.<br />
In this study the influence of suspension modelling on the accuracy of the<br />
simulation outputs is initially discussed based on results obtained using the<br />
four vehicle models described in section 6.4 and summarized schematically<br />
again here in Figure 6.52. The models shown can be thought of as a set of<br />
models with evolving levels of elaboration leading to the final linkage model<br />
that involves the modelling of the suspension linkages and the bushes.<br />
For each of the vehicle models described here it is possible to estimate the<br />
model size in terms of the degrees of freedom in the model and the number<br />
of equations that MSC.ADAMS uses to formulate a solution. The calculation<br />
of the number of degrees of freedom (DOF) in a system is based on the<br />
Greubler equation given in Chapter 3. It is therefore possible for any of<br />
the vehicle models to calculate the degrees of freedom in the model. An<br />
example is provided here for the equivalent roll stiffness model where the<br />
degrees of freedom can be calculated as follows:<br />
Parts 9 6 54<br />
Rev 8 5 40<br />
Motion 2 1 2<br />
Σ DOF 12<br />
In physical terms it is more meaningful to describe these degrees of freedom<br />
in relative terms as follows. The vehicle body part has 6 degrees of freedom.<br />
The two axle parts each have 1 rotational degree of freedom relative to the